US7469478B2 - Coupling and angular position measuring device using the coupling - Google Patents

Coupling and angular position measuring device using the coupling Download PDF

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Publication number
US7469478B2
US7469478B2 US11/448,499 US44849906A US7469478B2 US 7469478 B2 US7469478 B2 US 7469478B2 US 44849906 A US44849906 A US 44849906A US 7469478 B2 US7469478 B2 US 7469478B2
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Prior art keywords
coupling
tabs
base elements
support points
node areas
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Expired - Fee Related, expires
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US11/448,499
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US20060277771A1 (en
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Johann Mitterreiter
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Dr Johannes Heidenhain GmbH
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Dr Johannes Heidenhain GmbH
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Assigned to DR. JOHANNES HEIDENHAIN GMBH reassignment DR. JOHANNES HEIDENHAIN GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MITTERREITER, JOHANN
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
    • G01D5/00—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable
    • G01D5/26—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light
    • G01D5/32—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light
    • G01D5/34—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light the beams of light being detected by photocells
    • G01D5/347—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable characterised by optical transfer means, i.e. using infrared, visible, or ultraviolet light with attenuation or whole or partial obturation of beams of light the beams of light being detected by photocells using displacement encoding scales
    • G01D5/3473—Circular or rotary encoders
    • G01D5/34738—Axles; Driving or coupling means

Definitions

  • the present invention relates to a coupling for connecting two component parts, e.g., a compensation coupling that is rigid against rotation, which acts elastically in the axial and radial directions.
  • the present invention also relates to an angular position measuring device which includes such a coupling.
  • Angular position measuring devices also referred to as shaft encoders, are used for measuring rotary motions of a rotationally mounted member, e.g., a shaft, over one or more revolutions (multiturn functioning). In so doing, the rotary motion is recorded incrementally or absolutely.
  • linear motions can also be measured by an angular position measuring device.
  • a coupling is described in PCT International Published Patent Application No. WO 01/02808 that has four links or tabs which are each offset by 90°.
  • two opposite links that are aligned in parallel are each fastened to the same component part.
  • This arrangement is believed to have the disadvantage that, among other things, the respective coupling may require a great deal of space comparatively speaking, for angular position measuring devices having large shaft diameters (e.g., for those having hollow shafts for accommodating a shaft that is to be measured).
  • Example embodiments of the present invention may provide a coupling that has excellent mechanical properties, requires a comparatively low construction volume and is extremely economical to produce. Furthermore, a precisely operating angular position measuring device may be provided, which has comparatively small external measurements, even for large shaft diameters.
  • the coupling may be used for the connection of two component parts that is axially and radially elastic, but torsion resistant, the coupling including base elements and a plurality of tabs that are integrally formed with the base element at the node areas.
  • Each tab has at least two points of support that are distanced from each other in the circumferential direction.
  • one of the node areas is between points of support in the circumferential direction, one node area forming the connection of a tab to a base element.
  • at least one of the tabs is able to be fastened at its points of support to one of the two component parts, and at least an additional one of the tabs is able to be fastened at its points of support to the other of the two component parts in a rigid manner.
  • Both the node areas and the tabs are configured such that the latter are considerably more flexurally soft than the base elements.
  • the flexural softness refers substantially to the reaction of the node areas and the tabs to an initiation of radially or axially directed forces.
  • the tabs are connected to the base elements via the node areas, e.g., similar to the members of a pin-joined frame, which are connected to one another via a punctiform node.
  • the node area may be reduced to a punctiform node.
  • the node area is similar to a flexurally soft solid joint.
  • the angle enclosed by adjoining base elements may change in response to stress during the operation of the coupling.
  • the points of support at the appertaining tabs may be at a distance T from one another, the corresponding tabs being integrally formed with the node areas, all the way over a length t.
  • the ratio T/t of the distance T to length t may be least 3, e.g., at least 5, e.g., at least 7 or 8.
  • the tab may also be integrally formed at the corresponding node area, while having interrupted recesses or being perforated over the length t.
  • the coupling may be arranged such that in each case in the radial direction, the node areas have a smallest extension x, and the base elements a greatest extension R, the ratio R/x amounting, e.g., to at least 1.75, e.g., at least 2, and, e.g., at least 2.5 or at least 3.
  • points of support refer to geometrical areas in which the tab is able to be fastened rigidly to an additional component part.
  • the coupling may be made of one. and the same material, for example, of metal, e.g., steel, and, it may be formed in one piece of sheet metal.
  • the coupling may be arranged to be flat, e.g., made from flat sheet metal. Accordingly, the coupling may not be a spatial object, e.g., not a sheet metal part that is spatially bent.
  • a large, unobstructed inside diameter of the coupling may be achieved, without excessively increasing the outer dimensions of the coupling or the entire angular position measuring device.
  • the unobstructed inside diameter may also be seen as a free opening, for a shaft, for example.
  • the coupling may be constructed geometrically such that the unobstructed inside diameter amounts to at least 60%, e.g., at least 70%, of its maximum outside diameter. Despite this relatively large unobstructed inside diameter, the coupling may nevertheless be exceedingly torsion resistant.
  • the coupling may include a number 2 ⁇ n of tabs and/or base elements, n being a natural number greater than or equal to 3, e.g., equal to 4 or 5.
  • a coupling for a connection of two component parts that is radially elastic and torsion resistant includes: base elements; and a plurality of tabs integrally formed with the base elements at node areas, the tabs including two support points at a distance from one another in a circumferential direction, each node area arranged between support points and forming a connection of the tabs to the base elements, at least one of the tabs rigidly fixable at its support points to a first one of the component parts and at least another one of the tabs rigidly fixable at its support points to a second one of the component parts, the node areas and the tabs flexurally softer than the base elements.
  • the tabs may include two support points at a distance from each other, the tabs may be formed integrally to the node areas over a length, and a ratio of the distance to the length may be at least 3, e.g., at least 5.
  • a ratio of a greatest extension of the base elements in a radial direction to a smallest extension of the node areas in the radial direction may be at least 1.75, e.g., at least 2.5.
  • the coupling may be arranged centrosymmetrically with respect to a center, and the base elements may be arranged closer to the center than the tabs.
  • the coupling may include a number 2 ⁇ n of tabs, n being a natural number greater than or equal to 3.
  • the coupling may include a number 2 ⁇ n of base elements, n being a natural number greater than or equal to 3.
  • An unobstructed inside diameter of the coupling may be at least 60% of a maximum outside diameter of the coupling.
  • the coupling may be formed in one piece of sheet metal.
  • the coupling may be planar.
  • the tabs may be slotted.
  • the base elements may be geometrically arranged so that an extension of the base elements in a radial direction increases with increasing distance from the node areas.
  • the base elements may be arranged symmetrically with respect to a radially directed line.
  • an angular position measurement device includes: a first component part; a second component part, the first component part and the second component part displaceable with respect to each other; and a coupling fastened to the first component part and the second component part.
  • the coupling may be arranged as described above.
  • the angular position measurement device may include a hollow shaft.
  • the coupling may include an unobstructed inside diameter
  • the angular position measurement device may include a shaft penetrating the coupling all the way through the unobstructed inside diameter
  • FIG. 1 is a top view of a coupling.
  • FIG. 2 is a partial cross-sectional view of an angular position measuring device with the coupling.
  • FIG. 3 is an exploded view of the angular position measuring device.
  • FIG. 4 is a top view of an installed coupling without radial stress.
  • FIG. 5 is a top view of an installed coupling having radial stress, in which the deformations are not drawn to scale.
  • FIG. 1 is a top view of coupling 1 according to an example embodiment of the present invention.
  • Coupling 1 is formed in one piece of sheet metal, the outer contours having been cut out of 2 mm thick flat sheet metal by a punching process.
  • Coupling 1 includes six base elements 1 . 11 to 1 . 16 and six links or tabs 1 . 31 to 1 . 36 . Between base elements 1 . 11 to 1 . 16 , six node areas 1 . 21 to 1 . 26 are also arranged. At node areas 1 . 21 to 1 . 26 , tabs 1 . 31 to 1 . 36 are correspondingly integrally formed over a length t. Thus, the connecting area of the tabs 1 . 31 to 1 . 36 to the node areas 1 .
  • node area 1 . 21 is indicated by an elliptical dash-dot line.
  • Coupling 1 may be arranged centrosymmetrically with respect to a center M. As illustrated in FIG. 1 , in a corresponding manner, base elements 1 . 11 to 1 . 16 , tabs 1 . 31 to 1 . 36 and node areas 1 . 21 to 1 . 26 are all positioned centrosymmetrically with respect to center M. Furthermore, base elements 1 . 11 to 1 . 16 are arranged closer to center M than tabs 1 . 31 to 1 . 36 .
  • the symmetrical arrangement of coupling 1 has the result that deformations of coupling 1 are evened out in the operation of an angular position measuring device equipped with it, which may ultimately have a positive effect on the measuring accuracy of the angular position measuring device.
  • Coupling 1 has a comparatively large unobstructed inside diameter d.
  • the unobstructed inside diameter d in this exemplary embodiment is the diameter of the smallest circle around center M which touches the inner contour of coupling 1 .
  • outside diameter D is the diameter of the largest circle around center M which touches the outer contour of coupling 1 .
  • the unobstructed inside diameter d and outside diameter D are determinative sizes for the space required for coupling 1 and the angular position measuring device.
  • the ratio d/D amounts, e.g., to approximately 73%.
  • Radial direction corresponds to a direction that is directed outwardly away from center M
  • tangential direction corresponds to a direction orthogonal to the radial and the axial directions.
  • base elements 1 . 11 to 1 . 16 may be described as a triangle, whose two short sides are outside with respect to center M. The long side is aligned with the tangential direction (starting from the middle of the long side).
  • Base elements 1 . 11 to 1 . 16 also have a radial extension r, R, which decreases in the direction toward node areas 1 . 21 to 1 . 26 .
  • R radial extension r
  • base elements 1 . 11 to 1 . 16 are geometrically arranged so that their extension r; R increases with increasing distance from node areas 1 . 21 to 1 . 26 . Because of this geometrical alignment and arrangement, base elements 1 . 11 to 1 . 16 are exceedingly flexurally stiff with respect to tangential and radial forces.
  • base elements 1 . 11 to 1 . 16 are arranged symmetrically with respect to an imaginary, radially directed line, which extends through the intersection of the two short sides.
  • Each of the six tabs 1 . 31 to 1 . 36 has two support points 1 . 311 to 1 . 362 , that are distanced from each other by a distance T in the circumferential direction.
  • Support points 1 . 311 to 1 . 362 are arranged as square regions, each having a bore.
  • tabs 1 . 31 to 1 . 36 In order for tabs 1 . 31 to 1 . 36 to behave in a flexurally soft manner even when they are stressed by torsional forces, they are arranged to be comparatively narrow and long, and, in addition, they are slotted. The slots, and the bores also, are cut into the sheet metal by a laser process. Among other things, because of the comparatively great distance T and the narrow radial extension of tabs 1 . 31 to 1 .
  • tabs 1 . 31 to 1 . 36 are comparatively flexurally soft in the axial and the radial direction.
  • tabs 1 . 31 to 1 . 36 are narrower at their narrowest places in the radial direction than the largest radial extension R of base elements 1 . 11 to 1 . 16 . This property is supported by the slotted design of tabs 1 . 31 to 1 . 36 .
  • tabs 1 . 31 to 1 . 36 are described as including slots, it should be understood that tabs 1 . 31 to 1 . 36 may be arranged without slots, e.g., tabs 1 . 31 to 1 . 36 are slotless.
  • Each of node areas 1 . 21 to 1 . 26 is between two support points 1 . 311 to 1 . 362 , node areas 1 . 21 to 1 . 26 forming the connection of tabs 1 . 31 to 1 . 36 to base elements 1 . 11 to 1 . 16 .
  • the node areas 1 . 21 to 1 . 26 act as solid joints. Because of the correspondingly adapted geometrical arrangement of node areas 1 . 21 to 1 . 26 , a relative possibility of motion, substantially in the radial direction, is imparted to two adjoining tabs 1 . 31 to 1 . 36 and base elements 1 . 11 to 1 . 16 , while using the material elasticity.
  • node areas 1 . 21 to 1 . 26 have a smallest extension x in the radial direction, as illustrated in FIG. 1 .
  • the material strength in the radial direction in node areas 1 . 21 to 1 . 26 is considerably reduced.
  • Node areas 1 . 21 to 1 . 26 and tabs 1 . 31 to 1 . 36 are thus configured such that they are considerably flexurally softer than base elements 1 . 11 to 1 . 16 .
  • the flexural softness refers to radial and/or axial stresses.
  • the axial angular impulse of base elements 1 . 11 to 1 . 16 about radially aligned axes and about axial (orthogonal to the drawing plane of FIG. 1 , 4 or 5 ) axes is substantially greater than the corresponding axial angular impulse of node areas 1 . 21 to 1 . 26 and tabs 1 . 31 to 1 . 36 .
  • base elements 1 . 11 to 1 . 16 are arranged so that they taper toward node areas 1 . 21 to 1 . 26 , and that their extension r, R in the radial direction increases with increasing distance from node areas 1 . 21 to 1 . 26 .
  • the ratio T/t of distance T to length t is selected such that it amounts, e.g., to 9, in the example embodiment illustrated.
  • the ratio R/x of greatest extension R of base elements 1 . 11 to 1 . 16 to the smallest extension x of node areas 1 . 21 to 1 . 26 is approximately, e.g., 3.5, in this example embodiment.
  • coupling 1 may be exceedingly torsion resistant, so that, in response to tangential forces into support points 1 . 311 to 1 . 362 , practically no deformations may occur, which is of significance to an exact determination of the angular position.
  • FIG. 2 is a partial cross-sectional view of an angular position measuring device and its measuring technology apparatus.
  • the angular position measuring device has a bearing unit 3 , which includes as a component part an outer ring 3 . 2 and a hollow shaft 3 . 1 that is rotatable with respect to outer ring 3 . 2 .
  • rotatable hollow shaft 3 . 1 is arranged such that it penetrates coupling 1 all the way through unobstructed inside diameter d.
  • a scale disk 5 On hollow shaft 3 . 1 , there is a scale disk 5 , on which there is an angular division, or a scaling division, that is affixed by an adhesive in a torque proof manner.
  • a scanning board 4 is fastened to outer ring 3 . 2 , for example, by using screws.
  • a light source e.g., an LED 10 , sends light through a lens 11 and a scanning plate 12 furnished with a line graduation. LED 10 , lens 11 and scanning plate 12 are assigned in this context, to the stationary (not rotating) part of the angular position measuring device.
  • scale disk 5 is fastened to rotatable hollow shaft 3 . 1 .
  • scale disk 5 is able to modulate the incident light correspondingly to the angular setting of hollow shaft 3 . 1 .
  • the modulated light then impinges upon photodetectors of scanning board 4 .
  • Photoelectric signals result from this, which include the information concerning the angular setting of hollow shaft 3 . 1 .
  • the photoelectrically generated signals are processed further by electronic component parts on scanning board 4 .
  • the position signals that have been further processed are output via a cable 7 (see, e.g., FIG. 3 ) to an additional unit, for example, to a control device of a machine.
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • FIG. 3 is an exploded view of the angular position measuring device with coupling 1 .
  • Three tabs 1 . 31 , 1 . 33 , 1 . 35 of coupling 1 are connected to outer ring 3 . 2
  • screws are placed through the bores in support points 1 . 311 , 1 . 312 , 1 . 331 , 1 . 332 , 1 . 351 , 1 . 352 , and are screwed into inner threads of outer ring 3 . 2 .
  • three tabs 1 . 31 , 1 . 33 , 1 . 35 are rigidly fastened at their six support points 1 . 311 , 1 . 312 , 1 . 331 , 1 . 332 , 1 . 351 , 1 . 352 to bearing unit 3 , e.g., at outer ring 3 . 2 .
  • the other tabs 1 . 32 , 1 . 34 , 1 . 36 are rigidly fastened to another component part of the angular position measuring device, e.g., flange 2 .
  • the bores in support points 1 . 321 , 1 . 322 , 1 . 341 , 1 . 342 , 1 . 361 , 1 . 362 are provided with screws, and tabs 1 . 32 , 1 . 34 , 1 . 36 are correspondingly fastened rigidly to flange 2 .
  • adjacent tabs 1 . 31 to 1 . 36 are rigidly fastened in each case to a different component part, e.g., outer ring 3 .
  • a shaft that is to be measured may be mounted rigidly and torsion resistant in hollow shaft 3 . 1 of the angular position measuring device, while flange 2 may be firmly attached to a housing, and, in this context, alignment errors are compensated for, within admissible tolerances. This means that, during one revolution of hollow shaft 3 . 1 , motions of deformation occur in node areas 1 . 21 to 1 . 26 and tabs 1 . 31 to 1 . 36 , and both in the axial and the radial direction, as a function of the actually present errors.
  • coupling 1 may be described illustratively with reference to FIGS. 4 and 5 .
  • base elements 1 . 11 ′ to 1 . 16 ′ of coupling 1 have a geometry that is essentially rhombic, in the simulation model, in this example.
  • FIG. 4 illustrates the coupling in a state in which it is not stressed radially, and accordingly it also has no deformations. If, however, as a result of an alignment error, a radially directed force impinges upon the coupling, deformations are created, as illustrated in FIG. 5 , on an exaggerated scale. Support points 1 . 321 , 1 . 322 , 1 . 341 , 1 . 342 , 1 . 361 , 1 . 362 are rigidly fastened to one and the same component part. Because of the simulated misalignment, there is created a relative motion of this component part with respect to the other component part to which the remaining support points 1 . 311 , 1 . 312 , 1 .
  • both node areas 1 . 21 to 1 . 26 and tabs 1 . 31 to 1 . 36 are considerably softer flexurally than base elements 1 . 11 ′ to 1 . 16 ′.
  • the angles between adjacent base elements 1 . 11 ′ to 1 . 16 ′ are changed with respect to the unstressed state. For example, the angle between base elements 1 . 11 ′ and 1 . 12 ′ is increased, and in a manner so that base elements 1 . 11 ′ and 1 .
  • the coupling 12 ′ are quasi swiveled about an imaginary point in node area 1 . 22 . Still, as a whole, the coupling remains torsion resistant, axial errors and radial alignment errors being able to be compensated for. As described above, the coupling is arranged in a completely planar manner, radial and/or tangential forces not leading to any deformation in the axial direction. This behavior, in addition, contributes to a great torsion resistance.
  • ratio T/t of distance T to length also amounts, e.g., to 9, while the ratio R/x of the greatest extension R of base elements 1 . 11 ′ to 1 . 16 ′ to the smallest extension x of node areas 1 . 21 to 1 . 26 amounts, e.g., to approximately 4.5, in this example.
  • coupling 1 connects two component parts 2 , 3 of the angular position measuring device that are not rotatable (stator coupling)
  • example embodiments of the present invention are also applicable to angular position measuring devices in which the corresponding coupling 1 is used as a rotor coupling.
  • the coupling is rigidly fastened to two rotatable component parts, these rotatable component parts also being displaceable relative to each other.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)
  • Length Measuring Devices By Optical Means (AREA)
  • Transmission And Conversion Of Sensor Element Output (AREA)
  • Optical Transform (AREA)
  • Length-Measuring Instruments Using Mechanical Means (AREA)
  • Measurement Of Length, Angles, Or The Like Using Electric Or Magnetic Means (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Length Measuring Devices With Unspecified Measuring Means (AREA)
  • Insertion Pins And Rivets (AREA)
US11/448,499 2005-06-11 2006-06-06 Coupling and angular position measuring device using the coupling Expired - Fee Related US7469478B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005027071.9 2005-06-11
DE102005027071 2005-06-11
DE102006020067.5 2006-04-29
DE102006020067A DE102006020067A1 (de) 2005-06-11 2006-04-29 Kupplung und Winkelmesseinrichtung mit dieser Kupplung

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US20060277771A1 US20060277771A1 (en) 2006-12-14
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US (1) US7469478B2 (de)
EP (1) EP1757908B1 (de)
JP (1) JP5019793B2 (de)
CN (1) CN1877148B (de)
AT (1) ATE402398T1 (de)
DE (2) DE102006020067A1 (de)
ES (1) ES2309865T3 (de)

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US20080083849A1 (en) * 2006-10-04 2008-04-10 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20080083129A1 (en) * 2006-10-04 2008-04-10 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20080089756A1 (en) * 2006-10-13 2008-04-17 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20210003393A1 (en) * 2019-07-04 2021-01-07 Dr. Johannes Heidenhain Gmbh Angle measuring device and method for operating an angle measuring device

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DE102005013364A1 (de) * 2004-05-18 2005-12-15 Dr. Johannes Heidenhain Gmbh Positionsmesseinrichtung
DE102006020067A1 (de) * 2005-06-11 2006-12-14 Dr. Johannes Heidenhain Gmbh Kupplung und Winkelmesseinrichtung mit dieser Kupplung
EP2216630B2 (de) † 2008-11-24 2015-09-30 Pepperl + Fuchs Drehgeber GmbH Drehmomentstütze
DE102012207123A1 (de) 2011-04-29 2012-10-31 Koenig & Bauer Ag Bogenrotationsdruckmaschine mit mindestens einem direkt angetriebenen Zylinder
DE102011086462A1 (de) 2011-11-16 2013-05-16 Dr. Johannes Heidenhain Gmbh Winkelmesseinrichtung
DE102014002891A1 (de) * 2014-02-28 2015-09-03 Süddeutsche Gelenkscheibenfabrik GmbH & Co. KG Kupplungsvorrichtung, insbesondere für Industrieanwendungen
DE102019209862A1 (de) * 2019-07-04 2021-01-07 Dr. Johannes Heidenhain Gmbh Winkelmesseinrichtung
CN113091579B (zh) * 2019-12-23 2024-07-26 长春市春求科技开发有限公司 一种测量结合齿对称度和高度的检具
EP3945291A1 (de) * 2020-07-27 2022-02-02 Siemens Aktiengesellschaft Befestigungselement, insbesondere drehmomentstütze, und maschine

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EP1353150A2 (de) 2002-04-12 2003-10-15 Stegmann GmbH & Co. KG Drehwinkelmesseinrichtung
US6820511B2 (en) 2002-04-12 2004-11-23 Stegmann Gmbh & Co. Kg Apparatus for measuring rotational angles
US20060277771A1 (en) * 2005-06-11 2006-12-14 Johann Mitterreiter Coupling and angular position measuring device using the coupling

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080083849A1 (en) * 2006-10-04 2008-04-10 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20080083129A1 (en) * 2006-10-04 2008-04-10 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US7905029B2 (en) * 2006-10-04 2011-03-15 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US7967537B2 (en) 2006-10-04 2011-06-28 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20080089756A1 (en) * 2006-10-13 2008-04-17 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US8403606B2 (en) 2006-10-13 2013-03-26 Airbus Deutschland Gmbh Adjustment device for the alignment of supporting parts on structures having inherent dimensional tolerances
US20210003393A1 (en) * 2019-07-04 2021-01-07 Dr. Johannes Heidenhain Gmbh Angle measuring device and method for operating an angle measuring device
US11486740B2 (en) * 2019-07-04 2022-11-01 Dr. Johannes Heidenhain Gmbh Angle measuring device and method for operating an angle measuring device

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ATE402398T1 (de) 2008-08-15
CN1877148B (zh) 2011-06-22
EP1757908A1 (de) 2007-02-28
US20060277771A1 (en) 2006-12-14
DE502006001177D1 (de) 2008-09-04
CN1877148A (zh) 2006-12-13
EP1757908B1 (de) 2008-07-23
JP2006349168A (ja) 2006-12-28
ES2309865T3 (es) 2008-12-16
JP5019793B2 (ja) 2012-09-05
DE102006020067A1 (de) 2006-12-14

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